Ratchet powered tool



Nov. 25, 1958 w. A. BARNES RATCHET POWERED TOOL S VB w WIA/ 2 N PE wATTORN EYS Nov. 25, 1958 w. A. BARNES 2,861,488 8 RATCHET POWERED TOOLFiled Jan. 17, 1956 2 Sheets-Sheet 2 INVENTOR. %L AM A. BARNES BY MATTORNEYS United States Patent 0 T RATCHET POWERED TOOL William A.Barnes, Utica, N. Y., assignor, by mesne assignments, to Kelsey-HayesCompany, Detroit, Mich, a corporation of Delaware Application January17, 1956, Serial No. 559,605

7 Claims. (Cl. 81-15) This invention relates to cam actuated tools, andparticularly to a closable jaw hand tool of light weight and rigidconstruction for crimping or indenting workpieces such as electricalconnectors.

The primary object of this invention is to provide a movable jaw toolhaving a wide jaw opening, fast closure to a work position, highmechanical advantage through the work closing cycle, and assurance ofcompleting a full work cycle whereby the jaws are required to close to aspecific relative position before opening.

Subgenerically, an object of this invention is to provide a ratchetdevice for cyclic drive actuation wherein a ratchet is employed torotatably drive a revolvable wedge expanding device operating betweenseparable cam driven surfaces, and the wedge device comprising a seriesof rollable members in active surface contact with one another totransmit the reaction forces through the series across the work fieldwith little or no appreciable stress upon the mounting means carryingthe rollable devices upon the ratchet wheel. This drive device may beemployed for cam lever operation of any device operable by separable orshiftable cam driven surfaces.

A further object of this invention is to provide a ratchet device forsuch actuating mechanism, wherein the ratchet device is released over aportion of the work cycle thereof for rotation under forces acting uponthe ratchet device at the end of the work cycle and thereby produce aquick movement response allowing fast reopening of the actuated tool atthe end of the work cycle.

' When using plier-type tools for crimping electrical connectors andsevering heavy workpieces, or other similar high pressure jobs, it iscustomary to provide long handles to reduce operator fatigue, or tobringfthe' mechanical advantage to such a degree that thede'siredoperation is possible; Long handles or levers require less'input forceto do the required work and provide a high mechanical advantage.Lengthening the handles, however, introduces other undesirable factors.The longer the handle? the wider is the spread between the ends of thehandles, and this makes the long levered pliers unlikely for use incorifined quarters, more difficult to use, and induces early operatorfatigue. i i i Another object of this invention, therefore, comprisesthe provision of pliers having a large mechahicaladvam tage witha smallspan at 'the' ends of the openedleyers. Further objects are to provide ashort span lever actuated tool having a long lever characteristic, thejaws of which open wider than can .be expected of ordinary pliers ofsimilar size, and. to provide suchtool hayingthe foregoingcharacteristics which are relatively light in weight and which do notrequire close tolerances in manufacture that are difficult to obtain,inmass product-ion. V i .Still. a. further object of this invention isto providea aclosable jaw hand tool witli'both theidri've forcesjandtlierestraining reaction forces extending in short, "transverseandsubstantially parallel pathsacross the tool.

Pafiented Nov. 25, 1958 avariable rate of closure speed and ratio offorces in a tool having the desired transverse forces.

Other objects and a fuller understanding of the inven; tion may be hadby referring to the following description and claims, taken inconjunction with the accompanying drawings, in which:

Figure 1 is a side elevational view of a pivoted jaw tool designedprincipally for crimping electrical connectors, and being actuated bythe improved drive device of this invention;

Figure 2 is a sectional view taken along the line 2-}; of Figure 1;

Figure 3 is a side elevational view of a modification of web toolembodying three work producing jaws and driven by a planetary version ofthe drive device of this invention; V m

Figure 4 illustrates the tool of Figure 1 in its open'position assumedat the end of a work cycle and prior to the beginning of another workcycle; and,

Figure 5 is an operational illustration of the tool of Figure 1intermediate the maximum open position of Figure 4 and the full closedposition of Figure 1. I

In the past, reliance has been principally upon fulcrum type of tools,employing single or multiple fulcrums. Sometimes these tools have beensupplied with a link mechanism attached to the handles permitting avariable mechanical advantage. The well known bolt cutter is such a tooldesign. In this construction, handles are pivoted together and to therearward extensions of the opposed pivoted jaws. .The ratios'arefixed.Thejaws will not open wide to receive work. They have terrific power atcompletion of the closure but no variation from a uniform curve throughvarious" steps of closure andjrio guarantee that the "operator willcomplete the closure. This type of tool has stresses perpendicular tothe length of the tool;but provides no variation at the jaw from auniform curve of force. Such tools are heavy, rugged and the handlesmust be opened wide,"making them one stroke, two handed tools. l

Later developments brought about the use of tools having a fixedanviland a movable anvil. The movable anvil being generally actuated bymeans of a pivoted cam surface or ajack step device. Such devicesrequire rugged actuation structures because of the very large p te ma inti ifQII Y an s esses lac u n the su k 'ac ua id de c As'j r su a largein'Q f the input power is consumed in overcoming 'fnetro a lo 'ds andthe pivotal siupportingsurface s are subject o epidid te qra iva und hear n itiq t actually; breken jinder the extreme loa ng'; conditiosuhftoolsrequire'a stationary C type of frame with one actuatlugmeinberpushing againstthe C member." The Q 'frarrie has to, be heavy, and hasto be of heavy can sitruction far back into the body structure and thentlie Qjfr'ame springs under stress. This springing" hastens calculatedand' allowed for. The longer and r nore ir'i volve d thepath'of stressforces, the greater spring' aiid greaterjvariation ofdimension atclosure of the jaws with various sizes of warrants jaws. With simple,short path stresses across the tool, there will be inuch -less spring,and'iienceyar'iatioii'in closure witlrvaryingfl'o'ads l'lhe'presentinventio-n avoids the creation of any high And yet another objectof thislinvention is to provide reaction l'oads pon'auriving pivotmount, 'andconfiries the react-ion load withinFtliereacting'rnei'nbersth mselves; Qdriieduntljyfthe actuation device of the present invertti'drihas very lowniechanicallo'sses and little deterioration due tofrictional abrasion "Two cop en di" United States patent applicationsare finteresttd'nirnisha gene al aer r'dnna of in o matioii with regardto the problems solved by the present ivention. Thcse applicationsare;an applicatioricntitled Ratchet and Cam Actuated Tool" bearing SerialNo. 564,165, filed February 8, 1956, on an invention of Walter J Rozmus,and an application entitled Pivot Lever Retainer for Ratchet PoweredDevice bearing SerialNo. 562,253, and filed January 31),- 1956,disclosing an invention of William A. Barnes.

For the purpose of illustrating the present invention in an operativeand useful'structure, an electrical terminal crimping device has beenselected. As set forth in the drawings, the tool embodies a jaw 10 and ajaw 11 each having a conventional crimping forward end portion.

Two matched sets of half round dies are illustrated, although any workperforming construction may be substituted therefor.

, The jaws 10 and 11 are pivotally mounted by means of aninterconnecting link 12 having a pivot 13 mounting the jaw 10 and apivot 14 mounting the jaw 11. Extending from the pivot 13, the jaw 10has a drive receiving lever end 15, and the jaw 11 is provided with asimilar drive receiving lever end 16. Therefore, by driving the leverends 15 and 16 apart, a work closing force will be exerted upon the workends of the jaws 10 and 11. According to this invention, a cam actuatingdevice of improved construction provides such drive opening force.

n the inner side of the drive lever 15 there is provided a cam surface17. On the inner side of the drive lever 16 there is provided a camdriven surface 18. A spring 19, which is set forthonly in Figure 1 ofthe drawings in order to eliminate confusion from overlapping parts inthe remainder of the views, is employed to pull the levers 15 and 16together and urge the work portion of the jaws and 11 to an openposition. Spring 19 is only one such means of urging the jaws 10 and 11to a given position. Therefore, the maximum closed position of the drivelevers and 16, and the maximum open position will be considered to be awork field. The cam surfaces 17 and 18 are in opposed facingrelationship defining an included drive field therebetween.

' Figure 2 illustrates the actual construction of the illustratedembodiment, although this construction is not the only suitableconstruction. Figure 2 illustrates the fact that stampings are usedlargely as the structural parts. The ratchet and roller construction, tobe more fully described hereinafter, may here be seen to consist of adouble ratchet wheel with rollers therebetween.

In the two jaw version of the terminal crimping tool set forth in Figure1 of the drawings, there are illustrated three roller members 35, 36 and37 positioned in surface contacting series with one another across thedrive field between the opposed cam surfaces 17 and 18. Although threesuch rollers have been illustrated, it will be appreciated that anyplurality of odd numbered rollable members may be employed. Furthermore,the illustrated embodiment of the invention sets forth roller-bearingtype of rollable members, although rollable members such as balls may beemployed with suitable mounting and drive means. Nevertheless, thesurface of the rollers each contact the surface of the neighboringroller in the series. Thus, when the series is wedging between the camdriven surfaces 17 and 18, there will be no appreciable stress placedupon the mounting means for the rollable members, but rather the opposedreaction forces will be transmitted through the solid bodies of therollable members. Thus, as set forth in the operative positions of thetool in Figures 1 and 5, the series of rollable members acts as a solidmember. However, the full advantage of rollable members is achieved forreducing frictional drive losses and elimination of the wear that wouldnormally take place between sliding surfaces under high contactpressures.

A rotary ratchet device has been provided to revolvably drive the threerollable members in a work cycle. To this end, a ratchet wheel isrotatably mounted and serves as a carriage for the rollers 35, 36 and37. Stud bearings 38, 39 and 40 are employed to mount the three mentunder high pressure. Formation of the surfaces 17 and 18 is well withinthe scope and understanding of the qualified engineer. Note, however, aspreviously discussed, the position of the roller series in Figure 1 istransverse to the length of the tool, and generally parallel to a linethrough pivots 13 and 14. This position is an important feature of thisinvention.

To facilitate the handling of the tool, and to provide a manual drivefor the ratchet wheel 25, there is provided a handle 41 which is fixedand serves substantially no other purpose than to support the tool. Bycontrast, handle 42 is pivotally mounted on the tool and servesprincipally as a drive lever. Preferably, as a feature of thisinvention, the handle is pivoted on the same center as ratchet wheel 25.A pawl 43 is carried by the handle 42 and is positioned to act in thewell known manner of such pawl devices upon the ratchet wheel 25. Thistool can be used with a slow, powerful, one hand pro gression by openingthe handle enough to take one notch at a time. 'By using two hands andopening the handles Wider to take two notches, the progression speed isdoubled. A coiled spring 44 is employed to urge the handle lever 42 toan open position relationship with respect to handle 41.

However, the ratchet wheel 25 is not conventional in all aspects.Ratchet wheel 25 is provided with two separate series of ratchet teethindicated by the reference character 26 for one series, and thereference character 27 indicating the other series. Blank or toothlessareas 28 and 29 separate the tooth series 26 from the tooth series 27.

As may be readily understood by examining the Figures 1, 4 and 5 only areversal of the position of the roller series through 180 degrees isrequired to produce a complete work cycle. Therefore, a complete 360degree revolution of the ratchet wheel 25 will produce two complete workcycles.

Referring first to Figure 4 of the drawings, it may be observed that thelevers 15 and 16 are in their maximum closed position under the drive ofspring 19. The series of rollers is positioned in an angular directionbetween the closed levers 15 and 16. The form of the cam sur-v face 18is modified somewhat at the forward portion in order to permit maximumclosing with respect to the roller 37, whereas the length of the lever15 is foreshortened in order to permit the lever to drop down betweenrollers 35 and 36. Therefore, at the first revolving movement of theroller series, a fast opening action will result as the series ofrollers begins to wedge between the surfaces 17 and 18. This initialmovement produces fast closing of the work ends of jaws 10 and 11. Afterthe roller series has been revolved suflicient- 1y to position the endrollers 35 and 37 against the operative surfaces 17 and 18, orsubstantially in the position as shown in Figure 5, then the closingmovement is slowed considerably and is determined entirely by theprovided form of the surfaces 17 and 18. When the roller series issubstantially vertical between the ends of the levers 15 and 16,substantially as shown in Figure l of the drawings, the work ends ofjaws 10 and 11 are ing the roller series.

closed to their maximum closed position and the maximum force is exertedby the roller series between the levers 15 and 16. Nevertheless, verylittle if any stress is experienced by the bearing studs 38, 39 and 40carry- The reaction forces are carried through theseries between the twoopposed levers 15 and 16. This provides a very remarkable advantage 3)over previous actuation devices and results in very little frictionaldrive losses and surface disintegration. Further, the stresses arelateral and resisted by thelink .12, and link 12 is stressed in tension.

When the roller series revolves slightly past the maxi mum openingposition as set forth in Figure 1, ,the roller 37 will drop off of theend of lever 15, and the roller 35 will drop into the pocket on theforward end of the surface 18. The wedging action is lostinstantaneously. At this point, and under these conditions, if theratchet wheel 25 were fixed and restrained against free movement, therewould be a very great force on the bearing studs carrying the rollerseries, and fast opening action of the jaws would be prevented.Therefore, the blank areas 28 and 29 have been provided on the surfaceof the ratchet wheel 25 to allow free movement without overriding thepawl 43. The extent of the blank areas 28 and 29 is sufficient to permitthe roller series to resume the position shown in Figure 4 before thetooth series is again presented for contact by pawl 43. The rollerseries, now reversed 180 degrees, has completed one work cycle. It willbe readily apparent that the work cycle may be repeated a second timebefore a full 360 degree revolution has been completed by the ratchetwheel 25.

In order to prevent reversed movement of the ratchet wheel 25 byreaction forces between power steps by the pawl 43, a detent 45 ispositioned on the'forward area of the ratchet wheel and is urged againstthe tooth series by means of a spring 46.

In Figure 3 of the drawings there is illustrated a three jawmodification of the tool. The construction and operation is quitesimilar. In this modification two pivoted jaws 50 and 51, and a singlelongitudinally reciprocable jaw 52 are provided. Cam driving surfaces53, 54 and 55 on these jaws respectively are adapted and designed toreceive the three rollable members to permit the described closingaction upon revolution of the planetary series of rollable members to agiven position, and to open through a work cycle upon further rotationof this planetary series. The rollable members are in a planetaryarrangement wherein a center roller 56 is in surface contact with eachof three planetary rollers 57, .58 and 59. A three way compression of aworkpiece device may be achieved by this modification of the basicconcept.

Although the invention has been described in its preferred form with acertain degree of particularity, it is understood that the presentdisclosure of the preferred form has been made only by way of exampleand that numerous changes in the details of construction and thecombination and arrangement of parts may be resorted to withoutdeparting from the spirit and the scope of the invention as hereinafterclaimed.

What is claimed is:

1. A ratchet device for cyclic drive actuation, comprising, a pluralityof drive receiving members in spaced relationship, each drive receivingmember having a driven cam surface, each drive receiving member having awork cycle path, the plurality of driven cam surfaces jointly defining adrive field area, a plurality of rollable members in a planetary systemin said work field, said rollable members including planetary drivemembers to contact and actuate said driven cam surfaces and theremainder of said rollable members and in surface contact therewithbeing equidistant from the planetary members, said rollable membershaving surface contacting relationship across the planetary system totransmit reaction forces through the system for resistance externally ofthe system, and means to revolvably drive said planetary system in saiddrive field.

2. A ratchet device for cyclic drive actuation, comprising a pluralityof drive receiving members in spaced relationship, each drive receivingmember having a driven cam surface, each drive receiving member having awork cycle path, the plurality of driven cam surfaces jointly defining adrive field area, a plurality of rollable members in a planetary systemin said work field, said rollable members including planetary drivemembers to revolve and describe a circular outer path, said work fieldarea and said outer path related to cause revolving movement of theplanetary drive members to drive said drive receiving members throughtheir work cycle path, and the remainder of said rollable members beingequidistant from the planetary members and in surface contact therewith,said rollable members having surface contacting relationship across theplanetary system to transmit reaction forces through the system forresistance externally of thesystem, and rotary ratchet drive means torevolvably drive said planetary system in said drive field.

3. A power device for cyclic drive actuation, comprising, a first andsecond drive receiving member in spaced relationship, said first drivereceiving member having a first driven cam surface, said second drivereceiving member having a second driven cam surface, said first andsecond driven cam surfaces positioned in opposed relationship anddefining a drive field, a rotatable carriage, a plurality of rollablemembers carried by said carriage, said plurality of rollable membersbeing in surface contacting series position with one another across saiddrive field between said opposed first and second cam surfaces, wherebyrotation of the carriage will revolve the roller series as a cam deviceand reaction forces will be transmitted from one driven cam surface tothe other through the roller series with little stress upon the meansmounting the roller series upon the carriage.

4. A ratchet driven plier type tool, comprising, a first and second jaw,said first and second jaws each having a work end and a drive receivinglever end, pivot means intermediate each said jaw for transpositionof-operating force on the drive receiving lever into work force on thework end, said first and second jaw lever ends having first and seconddriven cam sufaces respectively and in opposed facing relationshipdefining an included drive field, a rotatable ratchet wheel, a pluralityof rollable members carried by said ratchet wheel, said rollable membersbeing in mutual surface contacting series position with one anotheracross said drive field between saidopposed first andrsecond camsurfaces, first and second handle members, pivot means mounting saidfirst handle member for swingable movement thereof, and pawl meapstransmitting swinging movement of said first handle into drive forceupon said ratchet wheel.

5. A closable jaw tool, comprising, first and second opposed pivoted jawmembers, said first jaw member having a work end and a drive receivinglever end with a first pivot mounting point intermediate thereof, saidsecond jaw member having a work end and a drive receiving lever end witha second pivot mounting point intermediate thereof, connecting meansjoining said first and second pivot mounting points and permittingpartial rotation of the jaws about the pivots, said drive receivinglever ends of the first and second jaws having opposed first and seconddrive receiving surfaces respectively for expansion drive to operatesaid jaws, said drive receiving surfaces defining a drive field,rotatable cam wedge means between said first and second drive receivingsurfaces, said first and second drive receiving levers and the rotatablecam wedge means formed to cooperate in producing a variable spreadingrate of the first and second drive receiving surfaces and a variablepower ratio with the maximum power ratio and minimum rate of movementoccurring with the cam wedge producing resultant forces across saiddrive field in a direction generally perpendicular to the longitudinalcenter line of the tool, the maximum stresses of operation thereforbeing generally transverse to the longitudinal center line of the tool,said rotatable cam wedge means comprising a planetary system of rollablemembers in mutual surface contacting series and means to drivinglyrotate said cam wedge means.

, 6. A power device for cyclic drive actuation, comprising, first andsecond drive receiving members in spaced relationship, said first drivereceiving member having a first driven cam surface, said second drivereceiving memmer having a second driven cam surface, said first andsecond driven cam surfaces positioned in opposed relationship anddefining an expandable drive field, a rotatable ratchet wheel, aplurality of rollable members carried by said ratchet wheel, saidrollable members being in a surface contacting series position with oneanother across said drive field between said opposed first and secondcam surfaces, and a pivoted lever with pawl means to actuate saidratchet wheel, said rollable member series having a first positionbetween said first and second drive receiving members wherein the drivereceiving members are in a maximum closed position thereagainst, saidrollable member series having a second position wherein the drivereceiving members are in a maximum open posi-' tion, said secondposition being about 90 degrees of rotation advanced from said firstposition, said first and second cam surfaces formed to drop out ofactive force receiving relationship with said rollable member seriesupon an advance thereof of the rollable member series to a. drivecessation position beyond said second position, said ratchet wheelhaving two separate tooth series separated by two blank spaces aroundthe periphery thereof, said tooth areas spaced to cease active contactwith said pawl upon driving said rollable series to said position ofdrive cessation, and spring means urging said first and second drivereceiving members closed upon said rollable series, whereby saidrollable series will rapidly rotate to the said first position thereofbut in a 180 degree rotated condition with respect to the prioroccupancy of said first position and the drive receiving members willcollapse to their starting position.

7. A pivoted jaw compression tool, comprising, first and second jaws, aconnecting link pivotally connecting the first and second jawsintermediate the ends thereof, the jaws therefore presenting first andsecond closable forward work ends and first and second rearwardlyextending drive receiving levers, said first lever having a first drivencam surface, said second lever having a second driven cam surface, saidfirst and second driven cam surfaces positioned in opposed relationshipand defining an expandable drive field, a rotatable ratchet wheel, threeroller bearings carried by said ratchet wheel in a straight line serieswith the center wheel on the center of rotation of the ratchet wheel andthe remaining two in surface contact with the center bearing, said twobearings describing a circular path upon rotation, said ratchet wheelhaving a diameter larger than said circle, said roller hearing seriespositioned in said drive field, a spring urging said first and seconddrive receiving levers closed upon.

said roller series, said roller series extending substantiallylongitudinally of the tool in the maximum open position of the jaws,said first and second driven cam surfaces formed to assume a maximumopen position to fully close the jaw work ends when the roller series isrotated to a lateral position substantially parallel to a line extendingbetween the pivotal connecting ends of said connecting link, said firstlever having a length extending to about the position of the rollerseries in said lateral position whereby further rotation of the rollerseries will cause the series of rollers and the levers to drop free ofone another and collapse to a starting position, said ratchet wheelhaving two sepaarte tooth series separated by two blank spaces aroundthe periphery thereof, said ratchet wheel mounted upon a center forrotation, a first handle for manual support of the tool, a lever handlewith pawl means to drive said ratchet wheel, said lever handle pivotedon the center of said ratchet wheel, said lever and pawl adapted to stepas far as two ratchet teeth at the discretion of the operator for fastinitial movement of the roller series, said tooth areas of the ratchetwheel spaced to end at the said pawl at the collapse position of thefirst and second levers and roller series, whereby a rapid return fromthe maximum closed jaw position to a starting position will take placefree of the pawl drive, and whereby two complete work cycles will takeplace for each full revolution of the ratchet wheel.

References Cited in the file of this patent UNITED STATES PATENTS1,024,432 Barron Apr. 23, 1912 1,278,849 Butterworth Sept. 17, 19182,339,880 Romanoif Jan. 25, 1944 2,413,178 Feltman Dec. 24, 19462,618,993 Carlson Nov. 25, 1952

